Rotary pump



March 2 1926.

O. C. GOERIZ ROTARY PUMP 3 Sheets-Sheet I .l

Filed 0ct. 18, 1922 1 575,048 March 2 1926. o. c GOERIZ ROTARY PUMP Filed Oct. 1 1922 :5 Sheets-Sheet 2 fn x mrolr Qrmr 61' 6067 52 0. C. GOERIZ March 2 1926.

ROTARY PUMP Filed Oct. 18, 1922 5 Sheets-Sheet 5 ill Patented Mar. 2, 1926.

UNITED STATES OSCAR C. GOEBIZ, 0F OAKLAND, CALIFORNIA,

no'rAaY PUMP.

Application filed October 18, 1922. Serial No. 595,434.

To all whom it may concern:

Be it known that I, OSCAR C. Gonnrz, a citizen of Germany, residing at Oakland, in the county of Alameda, State of Ca1ifornia, have invented a new and useful Rotary Pump, "of'which the following is a specification in such full and clear terms as will enable those skilled in the art-to construct and use the same.

This invention relates to a rotary pump and its object is to produce a pump which will combine features of the axial flow and centrifugal flow type pumps in the most efficient manner possible to produce a pump capable of having the maximum discharge areas for a given size of pump casing.

It will be understood by those skilled in the art that where pumps are intended to be used in wells of comparatively small diameter, say from 8" to 16, if the pump is a purely centrifugal type, the passageways for the water are of necessity very small, both upon the entrance and discharge sides. These small passageways limit the actual discharge and increase the friction to such an extent as to materially decrease the efficiency of such pumps.

Another object of the invention is to locate the point of fluid discharge of the runner at the hub, so as to give, when connected by a curve with the inlet point at the diameter of the hub substantially the same hydraulic pressure as that obtained at the outer curve of the blade developed along its cylindrical enclosing casing, thus preventing any currentswhlch reduce the pump efsmoothly curved blades gradually In furtherance of the object of producing a runner to obtain substantially the same hydraulic pressure across the entire cross section of the moving-body of water, and thereby increasing theefliciency of the pump, the curves of the blades along th hub and along the runner periphery are joined by changing from one extreme curve to the other extreme curve.

The other objects of the invention will ap car as the description proceeds.

n embodiment of the invention is shown in the accompanying drawings, in which the same reference numeral is applied to the same portion throughout, but I am aware that there may be modifications thereof.

smaller Figure 1 is a vertical sectional view of a pump made in accordance with the disclosure of this invention.

Figure 2 is a sectional view of a portion of the pump showing the runner lowered to reduce the pump capacity.

Figure 3 is a plan view of one of the runner blades, the dotted lines of the figure indicating radial lines of the pump runner.

Figure 4 is a plan view of therunner, the dot and dash lines indicating the lower edges of the runner blades while the solid lines indicate the upper and outer edges of the blades, the dotted lines indicating the curve along the hub.

Figure 4: is a runner.

Figure 5 is a side elevation of one of the runner blades.

Figure 6 is a View of one of the runner blades looking in the plane of rotation and looking toward its leading edge.

Figure 7 is a view of one of the runner blades looking from the center of the pump toward its periphery.

Figure 8 is a velocity dia ram indicating the conditions which must 0 tain along the flow lines of the impeller blades to combine the effects described.

Fig. 9 is a perspective view of a runner having seven blades drawn from an actual pump runner.

The pump is supported by any suitable fitting 1, which is placed at the top of the ground or upon any suitable frame work. This fittin supports a pipe 2 which extends to a suite le diffuser casing 3, or may be connected to other lengths of pipe in turn connected to the diffuser casing, if the depth of the well requires it.

Supported on the fitting 1 is a suitable frame 4, which carries an annulus 5, within which the thrust bearing 6 is adjustable. This thrust bearing has an inner flange 7 to retain the lubricant for the ball races 8, 9 and balls 10, but, of course, it will be apparent that any form of thrust bearing may be used in place of the one shown.

Resting upon the ball race 8 is a flanged hub 11. This hub is permanently secured to the shaft 12 by a suitable key 13 to support the shaft at any desired elevation, for the purpose of regulating the output of the pump without changing the speed of the bottom plan view of the pipes, if more than one length is used, in

any suitable manner, screw threads being shown in the present instance, and it has a plurality of curved diffuser blades 21, said blades being of any acceptable form to reduce the flow of water to the desired velocity. The cross sectional area of discharge of these .blades is greater than their cross sectionalarea of inlet at the bottom. They are connected to the outer'portion of the shell 3, and are connected at their inner edges to the frustrum of a cone 22. The outer portion of the shell 3 is swelled out at 23 to give the necessary outward flow lines to the water as it is discharged from the runner below.

The diffuser hub has bearings 24, 25 for the proper support of the shaft 12. w

The pump runner comprises a conical hub 26 which is connected to the shaft by means of a suitable key 27 and nut 28, and it has a plurality of blades 29 extending peripherally therefrom. These blades are developed to give equal lifts over all of the impeller surfaces along the varlous flow lines, assuming the efiiciency to be constant. TlllS construction will be given in accordance with the following mathematical formula.

Assuming the peripheral velocity V at the entrance and V" at the dischargeedge,

the tangential projection of the absolute velocities U and U" at both points, then all over the flow lines the condition V" multiplied by U minus V multiplied by U equals a constant; this will give substantially equal lifts all over the impeller blade surfaces.

Following out this formula develops a blade which gives substantially axial flow C at its entrance edge and a combined axial and tangential flow C" at its uppermost discharge edge with variations thereof at all intermediate points, the blade varying both in axial and radial pitch.

In order for the water to be directed to the pump runner without eddying, there 'is a bottom ring 31 secured on the bottom'of the casing 3, and it has vertical blades 32 to prevent eddying the water led to the runner blades 29. The pump runner blades 29 have their leading edges A extending from a point below the conical hub 26 upwardly and backwardly to connect with the hub in a plane indicated by the dotted line Figure 9 just about one quarter the height of said hub.. The outer edges of the blades are indicated at B and they extend substantially concentric with the runner axis to a point about one third their height below their tops at which place they turn sharply in toward the top of the hub as shown at C. (Note upperdotted line Figure 9.) The runners are, of course, cast with and connected to the hub forming a smooth curve D receding from the leading edges and then extending upwardly and outwardly to the top of the blades as shown in Figure 9. Now by observing the lower edges of the runner blades (Fig. l at the left) it will be seen that the only thing that portion of the blade up to the section line of the blade, can do (that point representing the narrowest portion of the opening between blades and casing) is to move 'the water axially. At that point the casing widens and the blade shape changes so the water can now pass laterally 'and upwardly into spaces between the diffuser blades 21. The water is discharged from the pump through the launder L.

With the present invention, an object is to produce a high capacity runner for large volumes and'high pressures, this high capacity being attained by the use of large entrance areas into which the water flows, principally axially, and by having the maxi mum diameter for the discharge substantially as large as the maximum inlet diameter of the runner, while the smallest diameter for the discharge is selected sufiiciently far above and inwardly from the stated point of the discharge, at the maximum diameter, to prevent choking of. the water, and to allow it to move along easy flow zones, as indicated at the dotted lines, Figure 1.

It thus follows from the above that the smallest discharge diameter is smaller than the maximum diameter at the inlet side of the runner for the standard capacity runner. Reductions in capacity of this standard runner are preferably made by lowering the runner from its normal position whereby the discharge area is reduced within the allowable limits of adjustment of the pump. The two effects are merged into one another by connecting the necessary extreme inner and outer curves by blades having gradual changes of direction from one form of curve to the other. This results in the production of a runner which has its blades to give axial flow to the. water at its periphery, while the blades at their inner portions, are so shaped as to give the necessary centrifugal flow to the water so that the pressure of the water traveling upwardly and outwardly along the inner portions of the blades will be substantially the same as the pressure of the water traveling upwardly along the outer periphery of the pump runner, thereby operating with the highest efliciency, intermediate portions of the blades being merged from one form to the other with. the gradual changes of direction, previously mentioned.

In the pump shown only one stage is indicated, but this pump is especially adapted merging to multiple stage operation since two, three or more of the shells 23 and associated parts may be coupled together when greater pressures are required than one stage can sup-.

ply. Only one bottom section 31 is used no matter how many stages are used.

What I claim is as follows, but various modifications may be made in the construction shown in the drawings and above particularly described form, within the purview of my invention.

1. In a turbinepump, blades, a runner adjacent the same, said runner having a frusto conical hub and bladescon'fiected therewith, which blades have theiri'surfaces adjacent the line of contact with said hub and their surfaces at their peripheries developed along different spirals, the blades having their lntermediate surfaces merged from one curve into the other with gradual changes of direction, and a casing within which said runner rotates.

2. In a turbine pump, a casing, a series of diffuser blades therein, a runner adjacent the conical hub with blades connected therewith,

which blades have their surfaces adjacent the hub and the surfaces at the periphery of the blades developed along different spirals, the intermediate surface of the blades from one curve to the other with and a cylin:

gradual changes of direction,

the

drical casing surrounding the blades, casin being enlarged above the blades.

4. n a turbine pump, a series of diffuser blades, a runner adjacent the same, said runner having blades developed along a hub a 'proaching a cone at their inner edges and a ong a flat spiral to, give a substantially axial and circular line of movement to the a series of diffuser different spirals, the inter-' fluid at their peripheries, and a cylindrical casing surrounding said blades.

5. A high pressure turbine pump impeller having blades peripheries of which are cylindrical, and a casing surrounding the same having 'a cylindrical bore within which the impeller rotates, diffuser blades carried by said casing, and means to vary the position of the impeller blades with respect to the diffuser blades whereby the discharge from the pump may be varied without varying the/speed of rotation of the impeller.

6. A high pressure turbine pump comprising a driving shaft, a conical hub carried thereby, spiral blades carried by said hub the outer edges of which blades are located in a cylinder, and a casing surrounding the impeller and within which it rotates, said casing being of greater interior diameter above the impeller than at the cylindfical portions of the impeller blades.

7. A high pressure turbine pump domprising a shaft, a conical hub carried tlfe reby, smaller at the inlet side, spiral blades carried by said hub, said blades projecting beyond the plane of the narrowest portion of said hub and tapering out to the periphery of the hub at its widest part, whereby substantiallyvthe same pressure over the entire surface of the impeller blades between the conical hub and the outer periphery thereof will be produced, and a cylindrical casing within which said impeller rotates.

8. Ahigh pressure axial flowing turbine pump for deep wells comprising a shaft, a

conical hub carried thereby smaller at the inlet portion, spiral blades connected with said hub, the outer edges of which terminate in a cylinder, and the lower ends of which are pointed and project below the narrowest portion of said hub, the upper ends of said blades tapering out into the widest part of the. hub, whereby substantially the same pressure over the entire surface of the impeller blades between the conical hub and theirperiphery will be produced, and a cylindrical casing within which said impeller rotates.

In testimony whereof I have hereunto set my hand this 10th day of July, A. D. 1922.

OSCAR C. GOERIZ. 

